Brake system

ABSTRACT

A brake system may include an actuating device, in particular a brake pedal; a first piston-cylinder unit having two pistons subjecting the brake circuits to a pressure medium via a valve device, wherein one of the pistons can be actuated by the actuation device; a second piston-cylinder unit having an electric motor drive, a transmission at least one piston to supply at least one of the brake circuits with a pressure medium via a valve device; and a motor pump unit with a valve device to supply the brake circuits with a pressure medium. The brake system may also include a hydraulic travel simulator with a pressure or working chamber which is connected to the first piston-cylinder unit.

CROSS-REFERENCE TO RELATED APPLICATION

This application is a Continuation of co-pending U.S. patent applicationSer. No. 16/625,228 filed Dec. 20, 2019, which is a Section 371 ofInternational Application No. PCT/EP2018/066436, filed Jun. 20, 2018,which was published in the German language on Dec. 27, 2018 underInternational Publication No. WO 2018/234387 A1, which claims priorityunder 35 U.S.C. § 119(b) to German Patent Application No. 10 2017 113563.4, filed Jun. 20, 2017, the disclosures of which are incorporatedherein by reference.

The invention relates to a brake system.

DESCRIPTION OF THE PRIOR ART

The trend towards vehicles with autonomous driving (AD) places highdemands on the brake system in terms of fault tolerance on the one handand redundant functions, e.g. for brake pressure generation, powersupply and computer functions (ECU) on the other. So-called one-box andtwo-box systems are favored. The latter consist of an electric brakebooster (BKV), a so-called e-booster, and an ESP system. This makes, forexample, the generation of brake pressure via electric motor andelectronic control unit (ECU) redundant for e-boosters and return pumpswith electric motor and ECU.

The known solutions have relatively long lengths and a high weight.

In WO2011/098178 (hereinafter referred to as variant A or as a follow-upbooster or e-booster), such a solution is described with a coaxial drivein which an electric motor acts via a gear and piston on the HZ piston(=main cylinder piston). The BKV control is effected via an electricalelement and reaction disc as a so-called follow-up booster, the pedaltravel is a function of the brake pressure and the volume absorption ofthe brake system, which requires long pedal travel in the event offading or brake circuit failure.

WO2009/065709 (hereinafter referred to as variant B, or as a follow-upbooster or e-booster) also shows an e-booster as a follower BKV. Herethe BKV control takes place via pedal travel and pressure. A separatepressure supply with electric motor and plunger acts via the amplifierpiston on the HZ piston.

WO2012/019802 (hereinafter variant C) shows an arrangement similar toWO2011/098178 with coaxial drive in which an electric motor acts on theHZ piston via a gear and piston. An additional piston cylinder unit isused here, which acts on a travel simulator piston (WS). The pedaltravel is thus independent of e.g. fading and brake circuit failure.However, the complexity and the construction length are high.

DE 10 2009 033 499 (hereinafter also referred to as variant D) shows abrake booster (BKV) with additional ESP unit with hydraulic actuation ofthe booster piston and external pressure supply. This arrangement withfour or five pistons and six solenoid valves (MV) is complex andunfavorable in length. The non-hydraulically acting travel simulator(WS) is located within the piston-cylinder unit upstream of the maincylinder and cannot be damped or switched via a solenoid valve (MV).

All above mentioned solutions have a redundant brake force amplification(BKV) function, because in case of failure of the BKV motor the ESP unitwith pump similar to the assistance functions with vacuum BKV guaranteesthe brake function in autonomous driving mode.

In the event of failure of the ESP motor, ABS shall function via thepossibility of pressure modulation by the BKV motor as described inWO2010/088920 of the applicant. However, this only allows a commonpressure control for all four wheels, which does not result in anoptimal braking distance.

All previously known one-box systems have a so-called travel simulator(especially for brake-by-wire) because of the advanced pedal travelcharacteristics.

The known systems with e-booster and ESP have only one redundancy in thepressure supply (DV), i.e. if the e-booster fails, there is a redundantpressure supply (DV) with redundant power for the brake booster (BKV) bythe ESP. Higher safety requirements are not taken into account. Also,sufficient ABS function is ensured by the e-booster if the ESP fails.

OBJECT OF THE INVENTION

Based on the prior art, it is the object of this invention to provide animproved brake system.

The invention is based on the object of creating a brake system for usein autonomous driving operation (hereinafter AD) and/or electricvehicles/hybrid vehicles with increasingly strong recuperation power(energy recovery by braking via generator/or drive motor in generatoroperation), which brake system is significantly improved as compared tothe prior art.

In addition, a cost-effective brake system for autonomous driving is tobe created, which fulfils all required redundancies as well as very highsafety requirements.

Furthermore, if the ESP should fail, both an adequate function of theABS in respect of braking distance and stability, and an adequatefunction of the recuperation are to be achieved with the brake system.

Solution According to the Invention

This object may be achieved by means of various aspects of the attachedclaims.

Among other things, the improvement is characterized in that the designof the brake booster has very few simple components with low tolerancerequirements (e.g. valves only in open/closed operation) and istherefore cost-effective, very short and narrow in design and enables aconstant pedal travel characteristic, especially with strongrecuperation.

Advantageous embodiments or designs of the invention are contained inthe further claims, the drawing and the figure description to whichreference is made here.

With the solution according to the invention and its embodiments anddesigns, a brake system is created which has a very short constructionas well as an advantageous pedal characteristic.

In particular, a two-box system is created according to the invention,having an electric brake booster which is connected to a standard ESPunit via two hydraulic lines (hereinafter referred to as X-Boost andESP/ABS unit, together referred to as two-box system), wherein the brakebooster has a pedal characteristic which is independent of the volumeabsorption of the brake system and the degree of recuperation.

Furthermore, the invention achieves a compact design of the brakebooster with a low box volume, which is very short and narrow and hasmany redundancies, e.g. for pressure generation, electrical supply,failure of the pump motor of the ESP unit and also includes an ABSfunction with reduced performance in the event of failure of the ESPunit. In emergency operation without ESP, the ABS function shouldinclude at least individual regulation axle-by-axle to improve thebraking distance (“select-low” pressure regulation).

The installation spaces in the unit compartment are becoming smaller andsmaller, thus the dimensions of the brake unit should be as small aspossible, especially in terms of width and length. This compact designis possible on the one hand by decoupling the main cylinder (HZ) pistonfrom the motor drive and on the other hand by a special short maincylinder (HZ) according to WO2016/023994 of the applicant, which isreferred to here with parallel arranged pressure supply (hereinafterpressure supply or DV) consisting of electric motor with piston drive.

The pressure supply (DV) is only effective up to the wheel locking limitof 80 to 100 bar. For higher pressures (e.g. for driver assistancefunctions), the pump of the ESP unit is switched on. This can thereforebe realized with the solution according to the invention in comparisonto variant A of the prior art described above, since the ESP pumpfunction has no influence on the pedal feel, since the brake pedal isdecoupled.

The purpose of the X-Boost with DV is to supply the corresponding volumeat maximum pressure of from 80 to 100 bar in order to increase thepressure of the ESP pump.

This has the advantage that the drive motor or the pressure supplydevice DV of the X-Boost with engine only has to be designed for a lowmechanical load, or the electric motor requires only low torque, forexample 80 to 100 bar, compared to the maximum pressure of approximately200 bar of the ESP pump. This enables a cost-effective ball screw drive(KGT) or a trapezoidal spindle with a plastic nut.

Secondly, the pump (ESP pump) can be designed such that the pump motoris loaded only by the differential pressure of 200 bar−(80 to 100) bar(=100 to 120 bar). A conventional ESP pump is loaded by the maximumpressure of 200 bar for example. This advantage means an advantagereduction of the power or torque of the pump motor.

There is also an additional possibility here for interconnection. TheESP pump may be switched on not only with activation of the X-Boost (80to 120 bar), but also in the event of rapid pedal movement at, forexample, 20 bar. This means either a quicker pressure increase fortime-to-lock (TTL) or additional power reduction of the motor of the DVof the X-Boost.

This connection of the pumps in series and/or parallel, in the case ofthe ESP pump, requires a twin-circuit gear pump, or, in the case of thepiston pump, an independent eccentric for each piston.

In the pedal characteristic, a retroactive effect from volumeabsorption, e.g. in the event of brake circuit failure, should beexcluded. On the other hand, it should be possible to generate a desiredpedal feedback, e.g. a small pedal movement when using the ABS function,optionally also intermittently. Faults, e.g. brake circuit failure, canalso be indicated by moving the pedal parallel to the warning lamp.

Various solutions are conceivable for the pedal travel simulator. In theentire pressure range (150 to 200 bar) the pedal travel simulator shoulddeliver a good pedal travel characteristic, e.g. up to 30 bar with aflat characteristic curve and then progressively increasing withoutinfluence whether the X-Boost or the ESP unit delivers the pressure. Inthe embodiment of the e-booster as a follow-up booster (variant Aaccording to the prior art), the pedal force characteristic curvechanges significantly during the transition from e-booster to ESP andrequires a lot of software effort for the PWM operation of the valvesnecessary for this. This is not the case with the solution according tothe invention, since the operation of the ESP pump has no influence onthe pedal characteristics, since the pedal is decoupled via the travelsimulator.

To reduce the construction volume, the return spring (18) can be used inthe flat part of the pedal travel characteristic curve, so that thevolume in the piston travel simulator is smaller and only corresponds tothe progressive part of the characteristic curve, as also shown inWO2013/072198 of the applicant, to which reference is made here.

The travel simulator can be advantageously a piston simulator (WS)connected to the working chamber of the auxiliary piston via a hydraulicconnecting line or/and a plunger simulator connected to a workingchamber of the second piston (SK). If a plunger simulator is provided,the control pressure dependent on the pedal travel acts on the plunger.

It is also advantageous if the travel simulator can be switched off in afurther development and is not effective in a first range and the brakepedal force is determined exclusively by a return spring and isdetermined in a second range by the return spring and travel simulatorpiston.

In addition, a switching valve can be connected upstream of the travelsimulator in order to switch the travel simulator on or off as required.However, if no switching valve is connected upstream of the travelsimulator, the switching valve (WA) must be arranged in a branch linebranching off from the pressure or working chamber of the auxiliarypiston to the travel simulator to the storage container.

It is also advantageous if the pressure-volume characteristic is usedfor pressure supply control and diagnostics.

Another possibility for the realization of a pedal travel simulator is aTHZ (=tandem main brake cylinder) with plunger without piston travelsimulator as described or illustrated in WO2016/023994 of the applicant,to which reference is made here in this respect. Here, the controlpressure to the BKV, which depends on the pedal travel, acts on theplunger and thus generates the pedal feedback effect.

Depending on the pedal position, pressure is transmitted from the pistonof the pressure supply to the SK piston of the main brake cylinder(T)HZ, which creates the brake pressure. The pressure supply consists ofan electric motor which drives the piston via a spindle. Both a ballscrew drive (KGT) and a trapezoidal spindle with nut can be used astransmissions. The latter is cheaper and quiet, but has a lowerefficiency and is self-locking. The latter has the advantage that in theevent of a failure in the pressure supply DV, e.g. of the engine, thepiston remains in the position so that there is no increase in volume inthe brake circuit under the influence of brake pressure.

For the ball screw drive (KGT), an additional shut-off valve must beused for this failure. The aspiration of the liquid from the storagecontainer (VB) takes place via a suction valve or via the piston sleeveseal with a breather bore, as in a main cylinder (HZ).

Access to the piston travel simulator can be closed with a solenoidvalve (WA), as in the event of a pressure supply failure (DV) the pedalforce acts on the main cylinder (HZ) and thus generates brake pressurein the so-called fallback level (RFE). Without the valve (WA), the pedaltravel in the fallback level (RFE) would be extended by the volumeabsorption of the piston travel simulator (WS).

Since the interconnection of X-Boost and ESP unit provides two redundantsystems for pressure generation with redundant power supply, thefallback level (RFE) is only effective during towing, actually only fordeep loading, e.g. in the event that the transmission of the vehicle maybe blocked. These facts allow greater degrees of freedom in system andpiston design, e.g. saving a WA solenoid valve.

One possibility for pad clearance control lies in providing a pad returnby means of a strong rollback seal of the wheel brake, which seal isable to produce the necessary clearance, in particular on account of thedeformation energy stored in it. The stored deformation energy generatesa return force which lifts the brake pad from the brake disc (clearanceor air clearance) as soon as there is no longer any pressure build-up inthe brake circuit. This is possible advantageously in the inventionsince there is no effect on the brake pedal due to the decoupling.

X-Boost and ESP unit preferably have separate power supplies, e.g. ESPis connected to a 12V battery and X-Boost is connected to a DC/DCconverter of a multi-voltage vehicle electrical system. Alternatively,both X-Boost and ESP unit can be connected to both 12V battery and DC/DCconverter. Thus both modules of the brake system of the two-box have aredundant power supply in each case.

The solution according to the invention has even more advantages overthe prior art variant A:

-   I. If the brake circuit fails, there is no pedal through fall;-   II. If the ESP motor fails, the pressure can also be controlled axle    by axle or wheel by wheel, which enables a considerable reduction in    braking distance;-   III. Many driver assistance functions can be implemented in X-Boost    and can be implemented with greater precision than in the ESP unit;-   IV. Recuperation control is easier, quieter and more accurate by    control via the DV than via inlet and outlet valves and the pump of    the ESP unit.

Pedal through fall I) can thus be avoided, since a leak in the systemhas no effect on the pedal feeling, since the travel simulator isdecoupled. In contrast to the solution according to the invention, aleak in the system has a direct effect on the pedal feeling in variantsA and B, for example, so that in the worst case the pedal travel issuddenly extended and the change cannot be controlled by the driver andleads to accidents.

The individual pressure regulation II) of axles and also wheel brakes ismade possible by the solution according to the invention because in theevent of failure of the ESP motor, the electric motor of the pressuresupply DV of the X-Boost takes over the pressure regulation and thepressure regulation has no influence on the pedal. This means that thereare considerably more degrees of freedom for axle-by-axle orwheel-by-wheel control than with follow-up booster solutions (variants Aand B). For this purpose, the pressure control of the invention via thepiston travel and motor current in accordance with (DE 10 2005 018649 ofthe applicant) and pressure gradient regulation (DE 10 2005 055751 ofthe applicant), to which reference is made here in this respect, is usedfor a high-precision pressure control which cannot be achieved withpulse width modulation (PWM) control of valves of the ESP unit.

The system decoupling (pedal of the system) is also of great importancefor the implementation of III) driver assistance functions, as describedin more detail below.

Recuperation control (IV) is becoming increasingly important due to theincreasing hybridization and spread of electric vehicles. The brakepressure is varied depending on the possible generator braking effectand the total braking effect required from the driver. This is calledbrake pressure blending. This may involve all wheel brakes (four-wheelblending), just one vehicle axle (two-wheel blending), or the singlewheel brakes individually. It requires appropriate brake pressurecontrol and valve control. This is described in detail in thedescription of the drawings.

The recuperation control (IV) in the solution according to the inventionis carried out exclusively via the piston travel control of the pressuresupply DV in the simplest solution (four-wheel blending). Depending onthe deceleration effect of the generator of the vehicle or the drivemotor of an electric vehicle operated in generator mode, a correspondingbraking pressure is set by adjusting the piston so that the sum of thehydraulic braking force and the braking effect by the drive motorresults in the desired total deceleration force.

This is possible in a completely variable manner, as the pressureposition of the pressure supply DV of the X-Boost has no effect on thepedal feel. This has considerable advantages, especially compared to thevariants A and B of the prior art, where the coupling between the pedaland the HZ volume means that the storage chambers of the ESP unit haveto be emptied in order to achieve a reduced deceleration whilemaintaining the same pedal feel. This requires an intervention in ESPand a very complex control of the outlet valves of the ESP unit. Inaddition, with the solution according to the invention, different ESPvariants for different brake circuit distribution (diagonal andparallel/brake circuits axle by axle, rear and front drives) can beavoided, since control takes place exclusively via the piston,independent of the brake circuit distribution and the drive type. Inparticular, the following advantages of the X-Boost also result from therecuperation.

Axle-by-axle blending (two-wheel blending or axle-by-axle blending) ismuch easier to implement, as will be described below in greater detail.

Some of the solution approaches according to the invention, inparticular the X-Boost, offer the following advantages in the pedal feelcompared to the prior art:

-   -   No change in pedal feel due to blending    -   No change in pedal feel due to changes in the brake system (e.g.        changes in brake release clearance, changes in PV characteristic        curve)

Blending by the X-Boost offers the following advantages in summary:

-   -   Precise adjustment of brake pressures, even with rapid changes        in generator torque=>Simple point braking;    -   No perceptible noises, e.g. from switching valves in the ESP        unit;    -   Blending in the entire vehicle deceleration range;    -   Much simpler software for blending than conventional e-boosters;    -   Uniform blending for diagonal (X) and axis-parallel (II) brake        circuit division;    -   Brake force distribution can be displayed at will, up to the        wheel lock limit. ESP interventions for vehicle stabilization,        especially on slippery and uneven road surfaces, and        interruptions of the recuperation process with complex switching        from recuperation to purely hydraulic braking and vice versa,        can thus be avoided;    -   Changes to the wheel brakes (e.g. pressure-volume        characteristics or p-V characteristics) on the non-driven axle        have no influence on the hydraulic braking;    -   No additional components required to hold hydraulic fluid (e.g.        no “smart actuator”);    -   No harder return spring required for pedal (important for        P_(max) in RFE); and/or    -   Changes in the PV characteristic curve of the brake system are        diagnosed.

In known systems according to variant A with follow-up booster, thepedal travel is a function of the volume take-up. To prevent the pedaltravel from becoming large during normal operation, it is necessary toadjust the dimensions of the main cylinder HZ for different vehicletypes with different piston diameters. In the event of a system failurein the fallback level RFE, this leads to high pedal forces with the samepedal travel in brake systems with greater volume absorption. Inaccordance with the requirements of ECE-13H, a vehicle deceleration ofat least 0.24-0.3 g is required for a maximum foot force of 500 N.

Some of the solutions according to the invention, in particular theX-Boost, allow the use of a small auxiliary piston diameter incomparison to the SK piston and thus higher brake pressures in thefallback level RFE at 500 N foot force. In addition, the volume in thebrake circuits can be further increased with brake fading in that DVcontinues to convey. This additional volume must be able to betransferred from the SK piston into the floating circuit, either by alarger diameter of the SK piston than the auxiliary piston or by alarger travel of the SK piston.

The BKV is controlled in one embodiment in accordance with DE 10 2005018649 and DE 10 2005 055751 of the applicant, to which reference ismade here in this respect, via the piston of the pressure supply DV byapplying a pressure in the brake circuit via a BKV characteristic curveas a function of the pedal travel. The pressure is measured in the ESPunit and provided by the pressure supply DV via a corresponding pistontravel. If the pressure sensor fails, this pressure signal is notavailable. The pressure sensor failure is detected by the pressuresupply DV via evaluation of the pressure volume characteristic curve(p-V characteristic curve). Here the corresponding pressure value ismissing for the piston travel.

The current measurement of the DV motor can also be used here as areplacement for the pressure measurement. In general, it is alsoconceivable to use only current measurement. For the correspondingaccuracy for pressure build-up and reduction, the hysteresis must beincluded in the characteristic curve of the pressure supply DV (pistontravel and pressure or current alternatively) by the friction forces inthe drive, optionally with correction values, e.g. by correlation of thecurrent with the vehicle deceleration.

The concept has further potential to increase function and error safetythrough:

a) Function

-   -   A small accumulator coupled to brake circuit 1 (BK1), also        called mini storage container, which enables the ESP pump to        build up further pressure in the wheel brake cylinders during        the suction stroke of the pressure supply (DV).    -   Hydraulic pedal force blending in the fallback plane

b) Safety

-   -   Use of an additional isolating valve (TV1) in brake circuit 1        (BK1) in case of failure of brake circuit 1 (BK1)    -   Dispensing with the travel simulator shut-off valve (WA). This        also eliminates its possible errors    -   Measures against blocking the sensor actuation    -   Linear level transmitter for brake fluid in the storage        container (VB), which detects small volume changes in the        storage container (VB) and can give an early warning in the        event of a leak in the brake system    -   Additional shut-off valve (36) in the hydraulic connection from        the auxiliary piston chamber to the storage container (VB)    -   Redundant seals with diagnostic option for main cylinder (THZ)        and pressure supply (DV)    -   Redundant measures, e.g. additional shut-off valve (MVs) in the        return line from the pressure supply (DV) to the storage        container (VB) in the event that the suction valve (28) fails.    -   Partially redundant control unit (ECU) for reading and        processing the sensor signals and for controlling the FV and PD1        valve    -   Heat dissipation from PCB to the main body, and thus to the        cooler spray wall, reduces the temperature of electronic        components and their failure rates    -   2×3-phase control of the motor, and thus redundant windings

This means that very high requirements for fail operational (FO) canalso be met.

In the following, further possible advantageous features are listed forthe possible embodiments described above, which can be added to theembodiments in combination or individually:

-   -   For example, the pistons of the first piston-cylinder unit (main        cylinder) may have different diameters and, in particular, the        auxiliary piston may be dimensioned smaller for adaptation to        smaller pedal forces in the fallback plane (RFE).    -   Likewise, one module of the two-box design (X-Boost/ESP) can be        connected to a 12V battery or 12V voltage supply and the other        module to a DC/DC converter or 48V vehicle electrical system or        other vehicle electrical system with higher voltage, wherein in        particular the X-Boost is supplied by the DC/DC converter or the        48V vehicle electrical system. To increase safety, both modules        can be connected redundantly to both vehicle electrical systems,        in particular a 12V battery and DC/DC converter.    -   The pressure supply transmission may have a self-locking        trapezoidal spindle with a self-locking action in the event of        drive failure.    -   The valve (FV) can be controlled by pulse width modulation (PWM)        to generate force feedback to the brake pedal (haptic feedback        with ABS).    -   A plug connection for the system may be located below the        storage container and directed inward towards the center of the        appliance to allow the associated plug to be pulled off        sideways.    -   The second piston-cylinder unit (pressure supply DV) can be        advantageously aligned parallel or perpendicular to the axis of        the first piston-cylinder unit (main cylinder).    -   By replenishment a larger volume of brake fluid can be made        available. This is advantageous in heavier vehicles or if there        are air bubbles in the brake fluid, or if there are vapor        bubbles in the brake fluid, which may arise as a result of        overheated brakes.    -   An improvement of the fault tolerance can be achieved by partial        redundancy of the control devices of ESP and X-Boost.    -   Adequate function over the braking distance and driving        stability if the ESP fails can be achieved by introducing        isolating valves (TV1, TV2) into the brake circuits (BK1, BK2)        and hydraulic multiplex operation of the pressure supply DC.        Recuperation for each brake circuit individually can thus also        be achieved. Further, the replenishment can also be implemented        in the brake circuit 2 (BK2).

DESCRIPTION OF THE FIGURES

Further features and advantages of the invention result from thefollowing description of embodiments examples of the invention and itsdesigns.

The drawings show as follows:

FIG. 1 : Complete X-Boost system with ESP;

FIG. 2 : Pedal characteristics;

FIG. 3 : Main components of the system;

FIG. 4 : Extended X-Boost;

FIG. 4 a : Redundancy in valve FV to increase functional security

FIG. 5 : X-Boost with measures to increase functional security

FIG. 5 a : Pedal travel sensor with measures to increase functionalsecurity

FIG. 6 : Pressure supply with additional valve to increase functionalsecurity

FIG. 7 : Pressure supply with seal redundancy to increase functionalsecurity

FIG. 1 shows a schematic diagram of the brake system with an actuatingdevice, in particular brake pedal 1, a first piston-cylinder unit THZ,which can be actuated by means of the actuating device, a secondpiston-cylinder unit with an electromotive drive and a transmission(hereinafter also X-Boost or booster) and an ABS/ESP unit. The ABS/ESPunit is known with the main components pump P with motor M, valves HSV1and HSV2, USV1 and USV2, inlet and outlet valves EV and AV assigned tothe wheel brakes, and storage chamber (SpK). This system is described inmany publications and patent applications. It is already on the marketas an e-booster and is mainly used in electric and hybrid vehicles,because here the brake system is controlled in conjunction with thebraking torque of the generator, i.e. recuperation. As is well known,both the e-booster and the ESP elements can play a role here, especiallyin the pedal characteristics. Another field of application is vehicleswith autonomous driving. The focus here is on error safety andredundancy of the functions, such as pressure supply and ABS function.The main difference in system design is the new X-Boost concept. Thisconsists of a special main cylinder HZ with travel simulator WS andpressure supply DV, which is arranged parallel or perpendicular to themain cylinder HZ in order to achieve a short overall length, see alsoFIG. 3 .

The main cylinder HZ essentially consists of an auxiliary piston (HiKo)16 and an SK piston (floating piston) (12) with return spring 12 a. Theauxiliary piston 16 is connected to a plunger 16 a, which acts through apartition wall 14 with seal into the pressure chamber 12 d. A distanceof approx. 50% of the travel of the auxiliary piston (HiKo) 16 isbetween the end of the plunger and the SK piston. The plunger (16 a) hasa significantly smaller cross-sectional area than the pistons of thefirst piston-cylinder unit (>factor 5 smaller) and contributesinsignificantly to pressure build-up and pressure sensing in the brakecircuit and transmits this force to the brake pedal, thus generating ahaptic feedback to the brake pedal, especially during ABS operationand/or fading.

Normally, a valve FV is closed at the start of braking and the auxiliarypiston HiKo acts on the travel simulator WS, whose function and variantsare described later. The auxiliary piston HiKo has two functions: fornormal operation and for a fallback level in the event of a failure ofthe pressure supply DV. In the first case, normal operation, it feedsthe travel simulator WS with the valve FV closed, and the pedal travelis the input signal for the pressure supply DV. At the fallback level,when the pressure supply DV fails, it also feeds the travel simulator WSwhen the valve FV is closed, but the pedal travel is now the inputsignal for the ESP booster.

When brake pedal 1 is actuated with pedal plunger 3, redundant pedaltravel sensors 2 a/2 b are activated simultaneously. These canadditionally be decoupled via an elastic member KWS, as described in DE11 2011 103274 of the applicant, to which reference is made herein thisrespect. Advantages are on the one hand detection when the auxiliarypiston (HiKo) 16 is blocked, and on the other hand the differentialtravel of the sensors when the auxiliary piston (HiKo) 16 is blockedprovides a control signal for auxiliary braking. The elastic member canalso be part of the spring characteristic of the WS travel simulator.The auxiliary piston (HiKo) 16 has a normal breather hole of a THZpiston which is connected to the storage container VB. It is well knownthat a brake circuit fails if the primary seal fails. This can beavoided by using a check valve RV which is used for venting and athrottle in the connection line to VB. The throttle is dimensioned witha small flow rate so that the pedal characteristic is not significantlychanged (3 mm pedal travel in 10 s) if the seal fails and can still bediagnosed. The same arrangement can also be used for the floating piston(SK) 12 (not shown), which makes the failure of both seals uncritical.Alternatively, a normally open solenoid valve can also be used in thefeedback line, which closes after pedal actuation or diagnosis. Thisapplies to both pistons of the HZ (auxiliary piston HiKo and the secondpiston SK).

The travel simulator WS can be designed in different ways. Theillustrated design corresponds to the prior art, which is described invarious patent applications, consisting of a WS piston with springcombinations, which as a function of the pedal travel provide the pedaltravel characteristics. The valve RV is used for the fast pressurereduction P_(ab) from the travel simulator WS, if the pedal is releasedvery fast, and the throttle D for the desired throttled pressurebuild-up P_(auf) with the corresponding pedal characteristics. Inaddition, the travel simulator WS can be switched off via the valve WA.This is necessary for non-redundant systems in the fallback level (RFE)so that the intake volume of the travel simulator WS does not affect thedelivery volume of the auxiliary piston HiKo to the brake circuit BK1and pressure chamber 12 d. With this system (FIG. 1 ) the ESP actsredundantly in case of failure of the X-Boost, where the ESP pump sucksvolume from the storage container via the main cylinder THZ and thepressure supply DV. The valve WA can therefore be dispensed with. Theauxiliary piston (HiKo) 16 with pedal plunger 16 a is moved to theinitial position by the pedal return spring 18 after brake actuation.

The pressure supply or DV is required for the BKV function. Thisconsists of an EC motor 8, which moves a piston 10 via a spindle 7 andnut and delivers pressure medium into the brake circuit BK1 and thepressure chamber 12 d. The dimensioning of the volume is derived fromthe BKV control, which controls a pressure from pedal travel 2 a/2 b viathe BKV characteristic curve, which is measured by the pressuretransducer DG in ESP. Alternatively, the motor current, measured via ashunt, can be used instead of the pressure. To improve the accuracy ofthe pressure control via the current measurement, this requires therecording of the friction losses in P_(auf) and P_(ab) in acharacteristic map, optionally additionally improved by correctionfactors, e.g. by comparison with the vehicle deceleration. This isparticularly important if the spindle drive is not a ball screw driveKGT, but a trapezoidal spindle with a plastic nut, for example.

In the starting position, the piston 10 has a breather hole 27 as in themain cylinder THZ. The volume can be sucked in via the sleeves or via asuction valve (SV) 28, which requires a lower vacuum to open and istemperature-independent.

If a trapezoidal spindle is used, the pistons remain in the position inwhich the motor drive no longer acts due to the self-locking of thepistons.

The dimensioning of the pressure supply DV can be staggered so that thefull travel of the DV piston corresponds to the volume consumption ofbrake circuit BK2 or the travel of the SK piston 2. The SK piston can bedesigned larger in diameter and also in travel for larger volumeintakes. The pressure supply DV, on the other hand, can be designedaccordingly or smaller in volume (piston and travel) by making themissing volume possible by replenishing with piston return travel viathe SV suction valve. For this a normally closed solenoid valve PD1 isrequired, which is not shown in FIG. 1 (see FIG. 4 ). For full volumecompensation in the event of pressure reduction P_(ab), the piston mustbe moved to its initial position with the breather hole open. Thesuction valve 28 and the breather hole 27 are connected to the returnline to the VB. All components of the pressure supply DV are combined inone housing 25.

The pressure build-up P_(auf) and pressure reduction P_(ab) in brakecircuit BK1 and brake circuit BK2 is achieved via the BKV control andpedal travel sensors, and the piston of the DV moves accordingly.Normally, the X-Boost pumps volume into the brake circuit BK up to theblocking limit 80-120 bar. If a higher brake pressure is required forfading, the X-boost volume pumps at 80-120 bar to the ESP pump, whichbrings about a higher pressure level. Previously, the ESP pump had to bedimensioned with corresponding conveying volume for full pressure, forexample 200 bar with ASR operation. By appropriate design of the pump,for example twin-circuit gear pump or separate eccentrics for the pumppistons and possibly additionally stepped pistons, the ESP pump only hasto handle the differential pressure between brake circuit pressure andX-Boost pressure, i.e. P_(Bremskreis) 200 bar)−X-Boost (=80−120bar)=80−120 bar, and therefore only 80-120 bar are necessary for thedesign of the ESP pump instead of 200 bar, and therefore a smaller ESPmotor is sufficient accordingly. In addition, with this design of thepump it is possible to arrange the E-Boost and ESP pump in parallelalready in the low pressure range, for example already from 20 bar, withrapid deceleration, which brings the potential for a quicker P_(auf)(TTL) or smaller X-Boost motor, accordingly.

If the pressure supply DV fails during a braking process, the DV pistonis pushed back under pressure in brake circuit BK1 so that the brakepressure can be completely reduced. If a self-locking gear is used forthe DV piston (trapezoidal spindle with plastic nut), such a pressurereduction is not possible. In this case, a normally closed solenoidvalve AV is provided in brake circuit BK1 with connection to the storagecontainer (not shown) or in connection from the breather hole of theHiko to the storage container VB.

In the event of failure of both electronic control or regulating units(ECU) of X-Boost and ESP, which occurs very seldom, volume is conveyedin the fallback level RFE by the auxiliary piston (HiKo) 16 to the brakecircuit BK1 and to the main cylinder HZ on the rear side of the SKpiston through the opened valve FV and the brake pressure is increased,wherein the brake pressure in the main cylinder HZ displaces the SKpiston and the pressure in brake circuit BK2 increases. To prevent thisvolume from escaping through the opened breather hole of the DV, anormally closed solenoid valve PD1 is provided (not shown in FIG. 1 ,see FIG. 1 a ).

Function in Case of Brake Circuit (BK) Failure

The failure of a brake circuit is detected by the pressure supply DV bycomparing the p-V characteristic curve of the brake system, which isstored in a characteristic map at certain intervals as part of adiagnostic cycle.

If, for example, the piston travel/volume is greater than the standardvalue, there is correspondingly air in the brake circuit BK or a leak.This can be identified via the p-V characteristic curve. In the event ofa leak, the leak can be identified by closing the four valves EV oneafter the other, provided this is located outside the units, e.g. in thewheel cylinder. If this is the case, for example, in brake circuit BK1,the valves EV of brake circuit BK1 are closed. The pressure supply DVthen acts via the SK piston into the brake circuit BK2 (correspondingdescription of the diagnostic logic in the patent applications DE 102015 106 089.2 and 10 2016 112 971.2, to which reference is made here inthis respect). If this does not work, the pressure supply DV fails, andso does the brake booster BKV. In this case, the ESP pump acts as brakebooster BKV in brake circuit BK2.

Failure of brake circuit BK2 does not result in failure of pressuresupply DV, as the SK piston (12) represents an important safety gatewith separation of brake circuits BK1 and BK2.

In both cases, the pedal characteristics remain the same and there is nopedal through fall.

ABS Function in the Event of Pump/Motor Failure in ESP.

When the ABS pressure reduction signal P_(ab) occurs, the DV controlcorrects the brake pressure to prevent the wheels from locking. Acorresponding pressure reduction P_(ab) in both brake circuits isnecessary to prevent a wheel from one of the two brake circuits fromlocking. However, this does not mean an optimal braking effect. However,this can be improved.

For example, during wheel locking with corresponding pressure reductionP_(ab) in one brake circuit, the other brake circuit cannot experiencepressure reduction P_(ab) by closing the valve USVs. This can beoptimized with individual wheel regulation by modifying the valves EVwithout parallel check valve RV as described in the patent applicationDE 11 2009 004636 (E112) to which reference is made here).

FIG. 2 shows the pedal characteristics over the pedal travel S_(p). Inarea A, the force increase with curve 1 is relatively flat up to approx.30 bar brake pressure, which corresponds to approx. 85% of all brakingoperations. This process can also be carried out via the pedal returnspring. Then the more progressive part B acts up to the blocking limit,followed by the range of higher pressures, e.g. for fading. Here thedriver should also feel that there has been a change in the brakesystem.

Curve 1 corresponds to the X-Boost with travel simulator WS. Without WS,i.e. with follow-up booster, curve 2 results where the pedal traveldepends on the venting state or fading. Accordingly, there is ascattering (not shown) to 2 a, which is even more extreme in the eventof brake circuit (BK) failure. With the conventional e-booster the BKVis switched from e-booster to ESP booster at x. This changes the pedalcharacteristics. Without influencing the BKV control, at the samepressure and pedal force, the pedal with the main cylinder (HZ) pistonwould deliver further volume to the ESP pump until the pressure in thewheel cylinders has reached its target values and the volume is returnedto the main cylinder HZ by overflowing the valves USVs.

A changed pedal characteristic with a larger pedal travel is achieved byreducing the amplification factor of the X-Boost, which results in theoutlined scatter band. Additionally, the valves HSV1 and HSV2 can bemodulated.

Here the X-Boost according to the invention with travel simulator WSbehaves like curve A with corresponding progressive force increase as afunction of the pedal travel.

Pedal Feedback with ABS

With the ABS function the pre-pressure supplied by the DV changesconstantly. This can be felt as a small force change on the plunger 16 aand thus on the connected pedal plunger 3, which is demanded by manybrake specialists. This can be changed at the beginning of the ABS orintermittently during deceleration by briefly increasing the inletpressure.

If the reaction is more noticeable, the FV valve can open and thecontrol pressure of the DV acts directly on the auxiliary piston HiKo.

Recuperation with Travel Simulator WS

The pedal characteristic is determined by the travel simulator WS. Here,brake management with generator determines the proportion of generatorbraking torque (electrical braking torque) and braking pressure(hydraulic braking torque) for the required vehicle deceleration. Bothquantities can be changed at will during deceleration, wherein therecuperation may apply a. the same brake pressure in all four wheelcylinders, b. axle-individual brake pressures at the vehicle axles, orc. wheel-individual brake pressures in all four wheel cylinders. Here,special control methods are necessary for the pressure supply DV, and,in the case of b. and c., possibly corresponding valve designs orcorresponding valve and pump control of the ESP unit.

The calculation of the brake pressure during recuperation in accordancewith a. is preferably based on wheel force. The required total brakingforce (target braking force) on the wheels is determined from the pedaltravel. If the target braking force can be applied electrically, thenthe hydraulic braking force is 0 N (braking pressure in the wheelcylinders 0 bar). If the target braking force exceeds the maximumpossible electrical braking force, the difference between the targetbraking force and the electrical braking force is the hydraulic targetbraking force. The hydraulic target braking force is realized by thepressure supply DV by pressure generation in the wheel cylinders. Forthis purpose, the individual Cp values of the wheel brakes are used tocalculate the target brake pressure, wherein the Cp value of a wheelbrake represents the ratio of brake force to brake pressure. The targetpressure is generated by a corresponding movement of the DV piston,wherein the pressure sensor of the ESP is used for the feedback of thepiston movement. In this way, the pressure supply DV can set the targetpressure both during pressure build-up and during pressure reduction.Due to the precise position control of the DV piston, the pressuresetting is very accurate. The pressure control with the DV is also veryquiet because no valves for P_(auf) and P_(ab) have to be actuated.Noise-causing valve and pump actuations of the ESP unit are notrequired. Furthermore, this recuperation control can be used uniformlyfor front, rear and all-wheel drive vehicles and X and II brake circuitsplitting. The pedal characteristic remains unchanged.

In the case of b. with axle-individual brake pressures at the vehicleaxles, the valves and the pump motor of the ESP might also have to becontrolled. If the target brake force exceeds the maximally possibleelectric brake force, the difference between the target brake force andthe electric brake force is thus the hydraulic target brake force, whichis first applied by the pressure supply DV only at the driven axle. TheEVs of the non-driven axle are closed. From a certain vehicledeceleration (for example from 0.2 g), the non-driven axle must also behydraulically braked (due to the stability of the vehicle underbraking). The hydraulic target brake force then has to be applied at thetwo vehicle axles jointly. The brake pressure at the non-driven axle isless than or equal to the brake pressure at the driven axle. Thepressure at the driven axle is increased by the DV when the EVs areopen. The pressure at the non-driven axle is adjusted by appropriate PWMcontrol of the EVs of the non-driven axle. If the hydraulic target brakeforce then has to be reduced, for example because the driver releasesthe brake pedal, or because the generator moment increases, the brakepressures at both axles are reduced. This occurs at the driven axle withopen valves EV by way of an appropriate control of the pressure supplyDV. The pressure reduction at the non-driven axle occurs by opening ofthe valves AV (possibly clocked), together with a control of the ESPpump and pulse width modulation (PWM) control of the valves (EV) of thenon-driven axle. The PWM control of the valves EV is intended to preventthe pressure at the rear axle from reducing too far. If, as a result,the pressure at the rear axle is reduced to 0 bar, the further reductionof the hydraulic target brake force then occurs exclusively via thepressure supply DV, with open valves at the driven axle and closedvalves EV and AV at the driven axle. The AVs of the driven axle remainpermanently closed during these processes. Valve and pump noise thusdevelops only above the specific vehicle deceleration (for example 0.2g) and only at the non-driven axle.

In the case of c. with the wheel-individual brake pressures in all fourcylinder, the valves and the pump motor of the ESP might also have to becontrolled. The control of the pressure supply DV, of the valves, and ofthe ESP pump is achieved similarly to the situation described under b.

Driver Assistance Functions

There are many driver assistance functions that require automatic brakeintervention, such as:

-   -   ACC (Adaptive Cruise Control) in which the desired vehicle        deceleration is set by active braking intervention.    -   AWB (Automatic Warning Brake) where a braking impulse should        wake the driver who has fallen asleep.    -   BDW (Brake Disc Wiping) where a very low brake pressure in the        wheel cylinders should wipe the water film off the brake discs        during rain so that the maximum braking effect is achieved        immediately during subsequent braking.

With these assistance functions, the pressure supply DV can generate thenecessary brake pressure in the wheel cylinders. The target brakepressure is specified by the various driver assistance systems. With theACC the target brake pressure is variable and depends on the requiredvehicle deceleration, whereas with the BDW the target pressure has asmall value (e.g. 1-3 bar). As with recuperation, the brake pressure isgenerated by a corresponding movement of the DV piston, wherein thepressure sensor of the ESP is also used here for the feedback of thepiston movement. As with recuperation, the brake pressure setting isvery accurate thanks to precise position control of the DV piston. Thepressure control with the pressure supply DV is also very quiet in thedriver assistance systems.

The figure description in FIG. 2 , in particular, shows the decisiveadvantages of the invention in addition to the overall length.

FIG. 3 shows the main components of the X-Boost in a spatialrepresentation:

-   -   Pedal plunger 3    -   Mounting flange BF on the front wall    -   First piston-cylinder unit or main cylinder HZ with pedal        interface    -   Motor 8 with housing pressure supply 1 (DV) 25, arranged        advantageously parallel to the main cylinder (can also be        aligned perpendicular to the axle of the HZ)    -   Hydraulic control and regulating unit HCU    -   Electronic control and regulating unit ECU    -   Storage container VB    -   The plug connector ST is located below the storage container VB        and above HZ and HCU and faces inwards towards the center of the        unit to allow the associated connector to be pulled out        sideways.

FIG. 4 shows an addition to FIG. 1 and FIGS. 1 a and 1 s based on thisdescription. The addition is the control unit (ECU) with interface tothe storage container (VB) and electrical connections e of sensors,solenoid valves and motor. The control unit (ECU) has a partiallyredundant partial control unit (ECU2) for actuating, for example,particularly safety-relevant components such as the FV valve withoptional separate vehicle electrical system connection. This partialcontrol unit (ECU2) in which, for example, the signals of the pedaltravel sensors (2 a, 2 b) are used, can preferably be integrated into anexisting ASIC with redundant power supply.

In the interface to the storage container (VB), the integration of thesensor element (33) into the printed circuit board (PCB) is providedwith floating body (34) and with target (T) in the storage container(VB). This allows an analogous evaluation of the level of the brakefluid in the storage container (VB) which supports the diagnosis of thesystem. If, for example, the level has decreased after pressure has beenbuilt up by the pressure supply (DV) and subsequent pressure reduction,a leak has occurred in the system.

The printed circuit board (PCB) is advantageously mounted on an aluminumplate or aluminum carrier (37) with good heat conduction to the mainbody (38) and spray wall (39). At peak loads, the outside temperature atthe control unit (ECU) can be 120° C. and at the spray wall (39) 60° C.,as the maximum temperature in the subsequent passenger compartment (39a) is 30° C. with cooling. This allows a considerable temperaturereduction to be achieved at the Mosfet (33 a), whose tub is transferredto the aluminum plate (37) via so-called vias (V). As is well known, thefailure rate of electronic components in particular is stronglytemperature-dependent according to Arrhenius law.

The EC motor (8) can be controlled via 2×3-phase control via a redundantconnection erect redundantly. The process is known. Usually the EC motor(8) requires an angle encoder as motor sensor (40).

The pressure supply DV has, here, an additional normally closed solenoidvalve PD1. This is necessary if the DV piston is pushed back underpressure in the fallback plane RFE and the corresponding volume is lostin the brake circuit BK1 and BK2. This may be compensated for by thelarge volume of the auxiliary piston HiKo, however this has a negativeeffect on the pedal characteristics. If the DV piston arrives in thestarting position, the breather hole opens, and brake fluid flows intothe storage container. In the fallback plane RFE the valve PD1 isclosed. In the case of ESP interventions or ESP boost, the valve PD1 canbe opened again.

As already explained in FIG. 1 , for the subsequent delivery of brakefluid volume into brake circuit 1 (BK1), volume is aspirated via thesuction valve (28) from the storage container (VB) by pulling back theDV piston (10). For this purpose, the valve PD1 is closed and the DVpiston (10) is retracted. The DV piston (10) draws brake fluid throughthe suction valve (28) and the hydraulic connection (R) from the storagecontainer (VB). When the redelivery volume is sucked into the DV chamber(10), the valve PD1 is opened and the DV piston (10) moves forward. TheDV piston (10) pushes the redelivery volume into brake circuit 1 (BK1).If during the suction phase of the pressure supply (DV) the ESP returnpumps (P, FIG. 1 ) actively increase the pressure in the wheel brakecylinders, negative pressure is generated in brake circuit 1 (BK1). Thevolume delivery of the ESP return pumps (P, FIG. 1 ) then stagnates andpossibly the ESP return pump (P, FIG. 1 ) in brake circuit 1 (BK1)aspirates an additional volume via seal D4, the replenishing bore (47)of the main cylinder (THZ) and the hydraulic connection (48) from thestorage container (VB). The SK piston (12) is pushed back by the SKpiston spring (12 a). The SK piston position then no longer correspondsto the pressure in the wheel brake cylinders, which can have a negativeeffect on the pressure reduction when the driver releases the brakepedal (1). A mini storage container (35) in brake circuit 1 (BK1) can beprovided to prevent this stagnation of the volume delivery or thisdisplacement back of the SK piston from happening. During the suctionphase of the pressure supply (DV), the mini storage container (35)provides volume for the ESP return pumps (P, FIG. 1 ). The requiredvolume of the mini storage container (35) depends on the duration of thesuction phase and on the volume delivery capacity of the ESP returnpumps (P, FIG. 1 ).

To increase the availability of the X-Boost and to check the function ofthe travel simulator (WS), a shut-off valve (36) can be provided in thehydraulic connection (44) between the replenishing bore (42) of theauxiliary piston and the storage container (VB). If, for example, theauxiliary piston seal (D2) is leaking, the shut-off valve (36) can beclosed, thus avoiding a failure of the travel simulator (WS).

The shut-off valve (36) can also be used to check various diagnosticfunctions. For this purpose, the valve PD1 is opened and the shut-offvalve (36) is closed. When the pressure supply (DV) is activated,pressure is applied to brake circuit 1 (BK1), wherein the pressure canbe measured, for example, with the pressure sensor (DG) of the ESP. Now,for example, the closing function of the travel simulator shut-off valve(WA) can be checked. If the valve FV is opened when the DV piston (10)is in constant position, the pressure in brake circuit 1 will drop onlyslightly when the travel simulator shut-off valve (WA) is functioningcorrectly. If the travel simulator shut-off valve (WA) is then opened,the pressure in brake circuit 1 (BK1) will drop considerably more if thefunction of the travel simulator shut-off valve (WA) is intact. If thereis a leak in the travel simulator shut-off valve (WA), the pressure inbrake circuit 1 (BK1) will drop considerably more, even if the travelsimulator shut-off valve (WA) is not yet activated, and will not dropfurther when the travel simulator shut-off valve (WA) is opened. If thepiston seal D6 of the travel simulator piston (49) is leaking, then thepressure in brake circuit 1 (BK1) continues to drop further afteropening the travel simulator shut-off valve (WA).

If the travel simulator (WS) fails, the valve FV is generally opened,e.g. if the valve FV leaks. When actuating the brake pedal (1), thedriver then pushes volume from the auxiliary piston chamber (43) to theESP return pump (P, FIG. 1 ) in brake circuit 1 (BK1). ESP can thenapply pressure to the cylinders via the active brake function of theESP, depending on the position of the pedal (1). The pedal travel issignificantly longer than with the intact X-Boost to achieve a certainpressure in the wheel brake cylinders. This can surprise the driver andlead to unpredictable behavior. To avoid this, a hydraulic pedal resetforce can be generated using the pressure supply (DV), so that the pedalforce is similar to the pedal force with the X-Boost function intact.For this purpose, the pressure in brake circuit 1 (BK1), and thus alsothe pressure in the auxiliary piston chamber (43), is adjusted by thepressure supply (DV) so that the normal pedal force/pedal travelcharacteristic of the travel simulator is reproduced as intended by thevehicle manufacturer. If this reproduction succeeds well, the driverwill not be surprised by a longer pedal stroke and his behavior will bemore predictable. In this example, the travel simulator (WS) willfunction as normal, but the brake pressure build-up by the pressuresupply (DV) in brake circuit 1 (BK1) can only occur after the auxiliarypiston sniff hole (45) is closed, or, if the shut-off valve (36) isused, also with smaller pedal travels. When using the active brakingfunction of the ESP, however, the pressure in the wheel brake cylinderscan already be increased before the auxiliary piston breather hole (45)is closed.

FIG. 4 a shows a measure to increase the functional safety of theX-Boost. The valve FV can be extended by FVred for redundancy,preferably with modified flow from the sealing ball to the valve seat.

FIG. 5 shows the entire system of X-Boost with ESP. X-Boost with THZ,the valves and the pressure supply DV corresponds to that in FIG. 4apart from an amended connection of the suction valve (28), as alsodescribed in FIG. 7 . FIG. 5 shows a redundant seal (D2.1) and areplenishing bore (50) for the auxiliary piston (16) with throttleddischarge (Dr2.1) to the storage container (VB). The throttle Dr2.1 isdesigned so narrow that if the seal (D2) leaks, only a small leakageflow is possible from the auxiliary piston chamber (43) through thereplenishing bore (50) to the storage container (VB), which, however,only results in a slow and small, non-interfering extension of thetravel of the brake pedal (1) during the limited braking time. Thisleakage flow is detected by the pedal travel sensors (2 a, 2 b) in aplausibility check, but also in a system diagnosis as described in E144.

A further seal D4.1 is also shown, as redundancy for the seal D4. Ifthis seal D4.1 fails, the brake circuit BK1 and the pressure supply DVwill thus also fail. In this case the ESP unit performs the task ofpressure supply, i.e. pressure increase. This can be avoided by thecombination of the seals D4 and D4.1 and replenishing bore 52, whereinthe connection of the replenishing bore 52 to the storage container, aswith the auxiliary piston (HiKo) 16, is provided with a throttle Dr4.1.A failure of this seal 4.1, with the low leakage flow through thethrottle D44.1, will not result in a failure of the brake circuit BK1 orthe pressure supply DV. In addition, a diagnosis of the seal D4.1 isadvantageously possible with this arrangement. Alternatively, a normallyopen valve TV can be provided in the connection to the storagecontainer, which valve can be closed in the event of a leak of the sealsD4 or D5.

For the seal D3, a redundant seal D3.1 with replenishing bore 51 andthrottle Dr3.1 can also be used. In addition, the travel simulator sealD6 can also be redundantly equipped with seal D6.1, replenishing bore 53and throttle Dr6.1. This means that all functionally important seals areredundant, and leaks can be detected during braking and diagnostics.This achieves a high level of safety for Fail Operational (FO). The sealarrangement can also be used with a one-circuit main cylinder (THZ) withpressure rod piston without floating circuit.

If brake circuit 1 (BK1) between ESP and the wheel cylinders of brakecircuit 1 (BK1) leaks, brake circuit 1 (BK1) and the pressure supply(DV) of X-Boost fails. There is also a risk that brake fluid may be lostto the environment due to leakage. As a remedy, ESP can close both inletvalves EV of brake circuit 1 (BK1). If the fault is detected in X-Boost,but X-Boost has no access to these valves (EV), then it must be switchedto the active brake function of the ESP. In this case, ESP adjusts thepressures in the wheel brake cylinders of brake circuit 2 (BK2). But forthe pressure adjustment in the wheel brake cylinders of brake circuit 1(BK1) ESP must constantly convey volume in brake circuit 1 (BK1). If ESPdoes not detect a leak in brake circuit 1 (BK1), brake fluid isconstantly lost. For this situation the isolating valve TV1 in brakecircuit 1 (BK1) between pressure chamber (12 d) of the main cylinder(THZ) and ESP is provided. If X-Boost detects the leakage in brakecircuit 1 (BK1), valve TV1 is closed. The pressure supply (DV) can thensupply the pressure chamber (12 d) of the main cylinder (THZ) and thusbrake circuit 2 (BK2) with pressure without losing brake fluid.

In addition, the valve TV1 can be used to provide optimized brakingdistance on slippery roads in the event of ESP failure. For legalreasons it is necessary that when braking on slippery roads, the wheelson the front axle lock in front of the wheels on the rear axle. For thisreason, the wheels on the rear axle are underbraked when the vehicledecelerates slightly. With X-Boost, the valve TV1 can be closed if thewheels on the front axle, on brake circuit 1 (BK1) with II brake circuitsplitting, show a locking tendency. Then the brake pressure in the wheelbrake cylinders at the rear axle, at brake circuit 2 (BK2), can befurther increased with the pressure supply (DV) of the X-Boost until thewheels at the rear axle also show locking tendency. This means thatalmost maximum deceleration can be achieved for a slippery road surface.Of course it is also possible to further increase the pressure in thewheel brake cylinders on the front axle by briefly opening the valve TV1after increasing the pressure in the wheel brake cylinders on the rearaxle. With X-brake circuit splitting, valve TV1 can be closed if thefront wheel of brake circuit 1 (BK1) shows a locking tendency. Aftervalve TV1 is closed, the pressure in brake circuit 2 (BK2) can befurther increased until the rear wheel of brake circuit 2 (BK2) shows alocking tendency. The pressure in brake circuit 1 (BK1) is so low thatthe vehicle still has sufficient stability, while the high pressure inbrake circuit 2 (BK2) causes a short braking distance.

In the feed line, BK2, from THZ to ESP, an isolating valve, TV2, is usedin the brake circuit 2 (BK2). As with the isolating valve TV1, thehydraulic connection is important, since the output of the valve seat isconnected to the ESP. These two isolating valves, TV1 and TV2, can beused for the following functions.

-   -   1. Replenishment, step 2. As already explained for FIG. 4 , the        volume in the brake circuit 1 (BK1), and thus the attainable        pressure level in the brake circuit 1 (BK1) and brake circuit 2        (BK2) is stopped by replenishment when the SK piston (12) in the        main cylinder (THZ) reaches its stop. A further pressure rise is        then still possible only in the brake circuit 1 (BK1). The stop        of the SK piston (12) is identifiable because the pressure in        the brake circuit 1 (BK1) now increases twice as quickly with        the volume increase in brake circuit 1 (BK1). If the stop of the        SK piston is reached, the isolating valves TV1 and TV2 are thus        closed and the piston (10) of the pressure supply (DV) is        retracted. The pressure in the brake circuit 1 (BK1) drops very        quickly. Under the influence of the return spring (12 a) of the        SK piston (12), the SK piston (12) moves back, possibly as far        as the starting position, and displaces volume from the primary        chamber (12 d) of the main cylinder (THZ) through the line of        the brake circuit 1 (BK1) and through the valve PD1 into the        chamber of the pressure supply (DV). At the same time, the SK        piston (12) sucks volume from the storage container (VB) into        the chamber before the SK piston (12) of the main cylinder via        the seal D5 of the SK piston (12) and via the bore (47) with the        hydraulic connection 48 of main cylinder (THZ) to storage        container (VB). Due to the modified connection of the suction        valve (28), the suction valve is not effective in the front        region of the piston (10) of the pressure supply (DV), and no        volume is sucked from the storage container by the suction valve        (28) and the connection R as the piston (10) of the pressure        supply (DV) moves back (see also description of FIG. 7 ). At the        end of this suction process, the isolating valves TV1 and TV2        are opened again. With the subsequent forward stroke of the        piston (10) of the pressure supply (DV), the SK piston (12) of        the main cylinder (THZ) is advanced again, and both the pressure        in the brake circuit 1 (BK1) and the pressure in the brake        circuit 2 (BK2) can be further increased. The pressure        supply (DV) is preferably controlled by the pressure        specification of the X-Boost.    -   2. The isolating valves, TV1 and TV2, can also be integrated in        the ESP as replacement of the switchover valves (US1, USV2),        with the above-mentioned precondition of the hydraulic        connection of the valve outlet to the wheel cylinder via the        inlet valve (EV). This is associated with a cost and weight        saving.    -   3. As already described, if the ESP fails, an ABS function in        brake circuit 1 (BK1) can be realized with the isolating valve        TV1 and the pressure supply (DV). Together with the isolating        valve TV2, an ABS function can be realized both in brake circuit        1 (BK1) and in brake circuit 2 (BK2). Should each wheel of a        brake circuit be ABS-controlled individually, the 4 inlet valves        (EV) may thus be used. This is of great advantage in particular        with a diagonal division of the brake circuit. The control        processes are not shown here. The pressure control is always        achieved by the pressure supply (DV).

A partially redundant control unit (partially redundant ESP-ECU) for themain control unit of ESP (ESP-ECU) can be used in the ESP for thecontrol of the inlet valves (EV) and also of the isolating valves (TV1,TV2). The function may preferably include the processing of the sensorsignals of the speed sensor and also of the yaw speed sensor for an ABSemergency function. This partially redundant control unit (partiallyredundant ESP-ECU), however, may also be connected to the control unitof the X-Boost (X-Boost ECU).

All control units (ECU) and partially redundant control units andpartially redundant control units (partially redundant ECU) have, inaddition to the connection to the vehicle electrical system (S1), aredundant connection to the vehicle electrical system with power supplyand bus systems (Sn). The partially redundant connections to the ESP aredenoted by the “cross in circle” symbol.

As already mentioned in the description of FIG. 4 , the control unit ofthe X-Boost (X-Boost ECU) may also have a partially redundant portion(partially redundant X-Boost ECU). This preferably supplies thefollowing components denoted by “circle”: pedal travel sensors (2 a, 2b), isolating valve FV, and DV valve PD1. It is also conceivable thatthis partially redundant control unit (partially redundant X-Boost ECU)also performs the tasks of the partially redundant control unit(partially redundant ESP-ECU) of the ESP, since the emergency functionof the ABS has to be provided also with the partially redundant controlunit of the X-Boost (partially redundant X-Boost ECU).

The ECU or partially redundant ECU each have a redundant connection tothe vehicle electrical system.

FIG. 5 a shows a solution for increasing safety using the example of thepedal travel sensor (2 a). If an extremely rare clamping of sensor 2 aoccurs when the brake pedal (1) is actuated, pedal movement is notpossible and the brake fails. A pretensioned spring (41 a) is providedinside the sensor (2 a), the plunger (2 a 1) of which can be movedagainst the pretensioning force of the spring (41 a) when the sensor (2a) is blocked. The error can be determined in a plausibility check ofthe signals of the two pedal travel sensors (2 a, 2 b) together with theelastic member (KWS). The two redundant return springs 18 a and 18 bacting when the brake pedal (1) is actuated replace the central returnspring 18. If the sensor 2 a is clamped when the brake pedal (1) isreleased, it may not be possible to release the brake pedal (1)completely. As a result, the vehicle would continue to be brakedcontinuously, contrary to the driver's intention. For this situation, anotch (2 a 11) is provided in the plunger 2 a 1, which is dimensionedsuch that under the influence of the plunger force, the plunger breaksat the point of the notch (2 a 11). Of course, this solution can also beused with the pedal travel sensor 2 b to increase the safety of thepedal travel sensor 2 a.

FIGS. 6 and 7 show a solution for the failure of the suction valve (28)of the pressure supply (DV), the failure of which, e.g. leakage, impairsthe function of the pressure supply (DV), since the volume in theworking chamber of the pressure supply (11) does not enter the brakecircuit 1 (BK1) via the valve PD1, but returns to the storage container(VB) via the suction valve (28) and return line (R).

Solution 1 (FIG. 6 ): Use a solenoid valve (MV) as a shut-off valve inthe return line (R) between the suction valve (28) and the storagecontainer (VB). If the leakage of the suction valve (28) is detected,the solenoid valve (MV) closes. The solenoid valve (MVs) can be openedto aspirate brake fluid into the DV chamber (11) through the pressuresupply (DV).

Solution 2 (FIG. 7 ): In an intermediate position of the DV piston (10)of the pressure supply (DV), an additional suction bore (46) and anadditional seal (D9) of the DV piston (10) are provided. The additionalsuction bore (46) connects the DV working chamber (11) to the storagecontainer (VB) via the suction valve (28) and the return line (R). As aresult, the suction valve (28) cannot act after the intermediateposition of the DV piston (10) when pressure is built up with the seal(D9) intact. The failure of the suction valve (28) then has no influenceon the pressure build-up function of the pressure supply (DV). When theDV piston (10) is moved back to the intermediate position, the DV piston(10) can only draw volume from the storage container (VB) via the sleeve(D9), the suction bore (46), the suction valve (28) and the return line(R), but with two pressure losses (the seal, D9, and the suction valve,28). Only before the intermediate position of the DV piston (10) doesonly the suction valve (28) work again. Since the suction function onlyworks during subsequent conveying, no further disadvantages can bedetected. Additional conveying is necessary if additional volume isrequired for a higher pressure level or to compensate for poorventilation.

Similar to the seal D4 of the main cylinder (THZ), a redundant seal D8.1with a breather bore (53) and throttle Dr8.1 can also be used for thepiston seal D8. Thus the pressure supply (DV) would also satisfy therequirements of the “Fail Operational” (FO).

It follows from the above description that the measures described indetail will lead to further modifications of the brake system accordingto the invention, which also belong to the claimed scope of theinvention.

LIST OF REFERENCE NUMERALS

-   1 Brake pedal-   2 a Master pedal travel sensors-   2 a 1 Plunger of the pedal travel sensor 2 a-   2 a 11 Notch in plunger 2 a 1 of pedal travel sensor 2 a-   2 b Slave pedal travel sensors-   2 b 1 Pedal travel sensor plunger 2 b-   3 Pedal plunger-   7 Spindle (KGT), trapezoidal spindle-   8 EC motor-   10 Piston (DV)-   11 Pressure chamber or working chamber of the DV-   12 SK piston-   12 a Return spring SK piston-   12 d Pressure chamber or working chamber on floating piston SK    (rear)-   14 Partition wall-   16 Auxiliary piston-   16 a Plunger-   18 Pedal return spring-   18 a Pedal return spring for pedal travel sensor 2 a-   18 b Pedal return spring for pedal travel sensor 2 b-   25 DV housing-   27 Breather hole-   28 Suction valve-   33 Sensor element-   33 a Component, e.g. MOSFET-   34 Floating body-   35 Mini storage container-   36 Shut-off valve for storage container (VB)-   37 Aluminum plate or support-   38 Main body-   39 Spray wall-   39 a Passenger compartment-   40 Motor sensor-   41 a Preloaded spring on pedal travel sensor 2 a-   41 b Preloaded spring on pedal travel sensor 2 b-   42 Replenishing bore of the auxiliary piston (16)-   43 Chamber of the auxiliary piston (16)-   44 Hydraulic connection-   45 Breather hole of the auxiliary piston (16)-   46 Suction bore in the pressure supply (DV)-   47 Replenishing bore of the main cylinder (THZ)-   48 Hydraulic connection-   49 Piston of the travel simulator (WS)-   50 Replenishing bore of the auxiliary piston (16)-   51 Replenishing bore of the auxiliary piston plunger (16 a)-   52 Replenishing bore of the main cylinder (THZ)-   53 Replenishing bore of the pressure supply (DV)-   AV Outlet valve ABS-   B1 Vehicle electrical system connection 1-   B2 Vehicle electrical system connection 2-   BF Mounting flange for end wall-   BK Brake circuit-   BK1 Brake circuit 1-   BK2 Brake circuit 2-   D Orifice for throttling-   DV Pressure supply-   DG Pressure transducer-   Dr 2.1-Dr 6.1, Dr8.1 Throttles in the return flow to the storage    container (VB)-   D1 Seal 1 of the auxiliary piston (16)-   D2 Seal 2 of the auxiliary piston (16)-   D2.1 Redundant seal (D2)-   D3 Seal of the auxiliary piston plunger (16 a)-   D3.1 Redundant seal (D3)-   D4 Seal 4 of SK piston (12)-   D4.1 Redundant seal (D4)-   D5 Seal 5 of SK piston (12)-   D6 Seal 6 of the travel simulator piston (49)-   D6.1 Redundant seal (D6)-   D7 Seal 7 of DV piston (10)-   D8 Seal 8 of DV piston (19)-   D8.1 Redundant seal (D8)-   D9 Additional seal of the DV piston (10)-   e Electrical connection-   e_(red) Redundant electrical connection-   ECU Control unit of X-Boost (Electronic Control Unit)-   ECU2 Partially redundant controller of X-Boost-   EV Inlet valve ABS-   FO Fail operational-   FV Isolating valve, normally open-   HZ Main cylinder-   KGT Ball screw drive (spindle)-   KWS Force-displacement sensor-   MVs Shut-off valve, normally closed-   PCB Printed circuit board-   PD1 Solenoid valve (normally closed) to the DV working chamber-   R Return to storage container VB-   R Return line to storage container VB-   RV Check valve at the breather hole of auxiliary piston-   vehicle electrical supply connection-   Sn redundant vehicle electrical supply connection-   SK floating circuit-   ST Plug connector-   SV Suction valve-   T Target-   THZ (Tandem) main cylinder-   TTL Time to lock-   TV1 Isolating valve, normally open, in brake circuit 1 (BK1)-   TV2 Isolating valve 2, normally open, in brake circuit 2 (BK2)-   TV Solenoid valve (normally open) to storage container (VB)-   V Vias-   VB Storage container-   WA Solenoid valve (normally closed)-   WS Travel simulator

What is claimed is:
 1. A two-box brake system for use in autonomousdriving operation and/or electric vehicles/hybrid vehicle, the vehiclehaving two axles, at least one of the axles being driven by at least oneelectric drive motor, each axle having a pair of wheel brakes assignedthereto, the two-box brake system comprising: an electric brake boosteras a part of a first box; an electronic stability control (ESP) unit asa part of a second box; first and second hydraulic lines arranged toconnect the electric brake booster to the ESP unit, wherein the firsthydraulic line is part of a first hydraulic brake circuit and the secondhydraulic line is part of a second hydraulic brake circuit, wherein theelectric brake booster comprises: a. an actuating device, in the form ofa brake pedal, b. a first piston-cylinder unit arranged to supplypressure medium to at least one of the first brake circuit or the secondbrake circuit, the first piston-cylinder unit arranged to be actuated bythe actuating device, c. a second piston-cylinder unit with anelectromotive drive, a transmission and at least one pressure supplypiston for supplying pressure medium to at least one of the first andsecond brake circuits, wherein the ESP unit comprises a valve devicehaving valves, a storage chamber, and a motor-pump-unit, arranged tosupply pressure medium to the wheel brakes, wherein the system isadapted such that, when braking, the at least one electric drive motoris switched into a generator mode and a generator braking effect isdetermined, wherein depending on the generator braking effect and arequired braking effect a braking pressure is determined, and whereinthe pressure for the wheel brakes is controlled by actuating the atleast one pressure supply piston and at least one of the valves of thevalve device of the ESP unit, whereby a two-wheel blending or asingle-wheel blending is implemented.
 2. The system according to claim1, wherein the valve device comprises at least one inlet valve, whereinthe inlet valve is controlled by pulse width modulation (PWM) forimplementing the two-wheel or single-wheel blending.
 3. The systemaccording to claim 1, wherein the first piston cylinder unit ishydraulically connected to a reservoir via a throttle and a check valve,wherein the throttle and the check valve are arranged in parallel. 4.The system according to claim 1, wherein the electric brake boostercomprises a printed circuit board, a reservoir, and a level sensor thatis arranged or integrated in or on the printed circuit board, whereinthe system is adapted to implement a linear evaluation of a liquid levelin the reservoir for early detection of leaks by means of the levelsensor.
 5. The system according to claim 1, wherein the firstpiston-cylinder unit is hydraulically connected to at least one of thebrake circuits via valve devices comprising a first feeding valve and asecond feeding valve, wherein the second feeding valve is arranged inseries with the first feeding valve in a hydraulic line connecting thefirst piston-cylinder unit with the first hydraulic circuit in such away that the first piston-cylinder unit is enabled to selectively beseparated from the first hydraulic circuit by one of the first or secondfeeding valves.
 6. The system according to one of the claim 1, thesystem further comprising a first isolating valve in the first hydraulicline arranged to secure pressure supply in the event of leakage of thefirst brake circuit.
 7. The system according to claim 6, the systemfurther including a second isolating valve in the second hydraulic linearranged to secure pressure supply in the event of leakage of the secondbrake circuit.
 8. The system according to claim 7, wherein at least oneof isolating valves is part of the ESP unit, wherein the at least one ofthe isolating valves that is part of the ESP unit replaces at least oneswitchover valve of the ESP unit.
 9. The system according to claim 7,wherein the system is adapted to control the isolating valves toimplement blending for the first and the second brake circuitsseparately.
 10. The system according to claim 1, wherein each of theelectric brake booster and the ESP unit comprises a respective firstelectronic control unit (ECU) and a respective second at least partiallyredundant ECU, wherein the first ECUs are connected to a first powersupply and the second ECUs are connected to a second power supply.
 11. Atwo-box brake system for use in autonomous driving operation and/orelectric vehicles/hybrid vehicle, the vehicle having two axles, at leastone of the axles being driven by at least one electric drive motor, eachaxle having a pair of wheel brakes assigned thereto, the two-box brakesystem comprising: a piston-cylinder unit with an electromotive driveand a transmission as a part of a first box; and an electronic stabilitycontrol (ESP) unit as a part of a second box, the brake system having,the ESP unit comprising a valve device having inlet valves, storagechamber, and a motor-pump-unit, to supply pressure medium to the wheelbrakes, wherein the piston-cylinder unit further comprises anelectromotive drive, a transmission, and at least one pressure supplypiston arranged to supply pressure medium to the ESP unit via a firsthydraulic line and a second hydraulic line, the first hydraulic linebeing part of a first hydraulic brake circuit and the second hydraulicline being part of a second hydraulic brake circuit, wherein the atleast one electric drive motor is adapted to be operated in a generatormode for braking the vehicle, and wherein a generator braking effect ofthe electric drive motor is determined at least in the generator mode,wherein depending on the generator braking effect and the requiredbraking effect a braking pressure is determined, and wherein pressurefor the wheel brakes is controlled by actuating the pressure supplypiston of the motor-pump unit with open inlet valves of the ESP unit toimplement a four-wheel blending.
 12. The system according to claim 11,wherein at least one pressure sensor in the motor-pump unit is used tocontrol actuation of the pressure supply piston.
 13. A two-box brakesystem for use in autonomous driving operation (AD) and; or electricvehicles/hybrid vehicle, the vehicle having two axles, at least one ofthe axles being driven by at least one electric drive motor, each axishaving a pair of wheel brakes assigned thereto, the two-box brake systemcomprising: a piston-cylinder unit as a part of a first box; anelectronic stability control (ESP) unit as a part of a second box; and afirst hydraulic line and a second hydraulic line disposed to connect theelectric brake booster and the ESP unit, the first hydraulic line beingpart of a first hydraulic brake circuit and the second hydraulic linebeing part of a second hydraulic brake circuit; the ESP unit comprisinga valve device having at least inlet valves, storage chamber, and amotor-pump-unit, arranged to supply pressure medium to the brakecircuits; the piston-cylinder unit having an electromotive drive, atransmission, and at least one pressure supply piston configured forsupplying pressure medium to the ESP unit, wherein the electric drivemotor is adapted to be operated in a generator mode for braking thevehicle, and wherein a generator braking effect of the electric drivemotor is determined at least in the generator mode, wherein depending onthe generator braking effect and a required braking effect a brakingpressure is determined, wherein pressure for the wheel brakes iscontrolled by actuating the pressure supply piston and at least one ofthe inlet valves of the valve devices of the ESP unit, whereby atwo-wheel blending or a single-wheel blending is implemented, andwherein the at least one inlet valve is controlled by pulse widthmodulation (PWM) for implementing a two-wheel or single-wheel blending.14. The system according to claim 13, further comprising a firstisolating valve in the first hydraulic line, which secures pressuresupply in the event of leakage of the first brake circuit.
 15. Thesystem according to claim 13, further comprising a second isolatingvalve in the second hydraulic line, which secures pressure supply in theevent of leakage of the second brake circuit.
 16. The system accordingto claim 15, wherein at least one of the first or second isolatingvalves is part of the ESP unit, wherein the at least one isolating valveof the ESP unit replaces at least one switchover valve of the ESP unit.17. The system according to claim 15, wherein the system is adapted tocontrol the isolating valves to implement blending for the first and thesecond brake circuits separately.
 18. The system according to claim 13,wherein the wheel brakes of the axle driven by at least one electricdrive are connected to the first braking circuit.
 19. The systemaccording to claim 13, wherein one of the axles is a non-driven axle,wherein, when braking the vehicle, pressure in the wheel brakes of anon-driven axle is in an increase phase adjusted by pulse widthmodulation (PWM) of at least some of the inlet valves.
 20. The systemaccording to claim 19, wherein the system is adapted to reduce ahydraulic brake force by: a) opening an inlet valve assigned to thewheel brakes of the driven axle and controlling the electromotive driveof the piston-cylinder unit; and/or b) opening outlet valves assigned tothe wheel brakes of the driven axle and controlling the motor-pump-unitof the ESP unit, wherein the inlet valves are controlled by pulse widthmodulation (PWM).
 21. The system according to claim 13, wherein theelectric brake booster and the ESP unit each comprises a respectivefirst electronic control unit (ECU) and a respective second at leastpartially redundant second ECU, wherein the first ECUs are connected toa first power supply and the second ECUs are connected to a second powersupply.
 22. The system according to according to claim 13, wherein theelectromotive drive is a 2×3-phase controlled electrically controlled(EC) motor with redundant connections.